Rotary vane device



United States Patent 3,181,510 ROTARY VANE DEVICE Robert W. Hovey, 19704 Cresthrook Drive, Saratoga, Calif. Filed Mar. 1, 1963, Ser. No. 262,131 4 Claims. (Cl. 12316) The present invention relates in general to rotary vane devices, and more particularly to a rotary vane motor.

An object of the present invention is to provide a rotary vane motor that is economical to manufacture without sacrificing durability.

Another object of the present invention is to provide a rotary vane motor of smaller dimension and of lesser weight Without sacrificing performance reliability.

Another object of the present invention is to provide a rotary vane motor with less moving parts and with greater volumetric displacement efiiciency.

Another object of the present invention is to provide a rotary vane device that is adaptable for use either as a pneumatic compressor, bi-fiuid pump, pneumatic expansion motor or as an internal combustion engine by merely varying the location of the ports.

Other and further objects and advantages of the present invention will be apparent to one skilled in the art from the following description taken in conjunction with the accompanying drawings, in which:

FIG. 1 is a front elevation of the rotary vane motor of the present invention with a rear cover plate thereof removed.

FIG. 2 is an axial section taken along lines 22 of FIG. 1.

Illustrated in FIGS. 1 and 2 is a two stroke cycle rotary vane device, motor or engine 113 of the present invention which comprises a housing 11. The housing 11 includes a cylindrical wall 12 formed with an axial bore therethrough, which bore defines a cylindrical chamber 12a. The cylindrical wall 12 may be considered a stationary outer cylindrical wall.

Fixed to one end of the cylindrical wall 12 is an annular rear cover plate 13 (FIG. 2) having a central bore 13a therethrough. At the opposite end of the cylindrical Wall 12 is secured a cylindrical front cover plate 14 (FIG. 2) formed with an axial bore 14a and a reduced diameter bore 14!). Nuts and bolts 15 secure the front plate 14, the cylindrical wall 12 and the rear plate 13 together to form a unitary structure for the housing 1 1.

Seated within the bore 13a of the rear cover plate 13 and projecting into the chamber 12a in fixed relation with the housing 11 is a non-rotatable shaft or stud (FIGS. 1 and 2). Supported for rotation by the portion of the shaft 20 projecting into the chamber 12a is a bronze bearing or suitable sleeve 21. The bearing sleeve 21 is freely rotatable about the axis of the non-rotatable shaft 20. It is to be observed that the shaft 21 is concentric with the cylindrical chamber 12a, the bronze bearing sleeve 21, and the cylindrical wall 12.

Supported by the bearing sleeve 21 for rotation about the axis of the fixed shaft 20 within the cylindrical chamber 12a is a nest of juxtaposed, close fitting vane holders 25-31, inclusive. Each vane holder includes a central opening, such as the central opening 25a (FIG. 1) for the vane holder 25, with the axis thereof coincident with the axis of the shaft 20 and the axis of the bearing sleeve 21. The diameter of the central opening of each vane holder is of a size to form a snug fitting relation with the bearing sleeve 21. Thus, the bearing sleeve 21 with the vane holders 25-31, rotate freely about the axis of the fixed shaft 20. The vane holder 25 is in sealing engagement with the rear cover plate 13.

The vane holder 28 (FIGS. 1 and 2) includes a slot 28a, which receives a vane (FIGS. 1 and 2) of rectan- 3,181,510 Patented May 4, 1965 gular cross-sectional area. The vane 35 is fixed to the vane holder 28 by suitable means, such as welding, for rotation therewith and extends in the axial direction. It is to be observed that the outermost wall 35a of the vane 35 is in continuous sealing engagement with the inner surface of the cylindrical wall '12 surrounding the cylindrical chamber 12a. The end surfaces of the vane 35 (FIG. 2) are in sealing contact with the facing surfaces of the cover plates '13 and 14, respectively.

As shown in FIG. 2, juxtaposed with opposite surfaces of the vane holder 28 are vane holders 27 and 29. The vane holders 27 and 29 have slots formed therein, (such as the slot shown in FIG. 1 for the vane holder 27), which receive a vane 36 of rectangular cross-sectional area. The vane 36 is fixed to the vane holders 27 and 29 by suitable means, such as welding, for rotation therewith and extends in the axial direction. The outermost wall 36a of the vane 36 is in continuous sealing engagement with the inner surface of the cylindrical wall 12 surrounding the cylindrical chamber 12a. The end surfaces of the vane 36 are in sealing contact with the facing surfaces of the cover plates 13 and 14, respectively.

Contiguous with the vane holders 27 and 29, spaced from the vane holder 28, are the vane holders 26 and 30, respectively. The vane holders 2-6 and 30 are formed with slots therein (such as the slot shown in FIG. 1 for the vane holder 26), which receive a vane 37 of rectangular cross-sectional area. The vane 37 is fixed to the vane holders 26 and 30 by suitable means, such as welding, for rotation therewith and extends in the axial direction. The outermost wall 37a of the vane 37 is in continuous sealing engagement with the inner surface of the cylindrical wall 12 surrounding the cylindrical chamber 12a. The end surfaces of the vane 37 FIG. 2) are in sealing contact with the facing surfaces of the cover plates 13 and 14, respectively.

luxtaposed with the vane holders 26 and 30, spaced from the vane holders 2'7 and 29, are the vane holders 25 and 31, respectively. The vane holders 25 and 31 are formed with slots therein (such as the slot shown in FIG. 1 for the vane holder 25), which receive a vane 38 of rectangular cross-sectional area. The vane 38 is fixed to the van holders 25 and 31 by suitable means, such as welding, for rotation therewith and extends in the axial direction. The outermost wall 38a of the vane 38 is in continuous sealing engagement with the inner surf-ace of the cylindrical wall '12. surrounding the cylindrical chamber 12a. The end surfaces of the vane 37 are in sealing contact with the facing surfaces of the cover plates 13 and .14, respectively.

The rotor vanes 35-38, inclusive, are similar in configuration, size and construction. (See rotor vanes 35 and 37 in FIGS. 1 and 2.) However, they are spaced apart substantially ninety degrees (FIG. 1). The vane holders 2531, inclusive, are similar in configuration, size and construction. (See vane holders 25 in FIG. 1.) However, the vane holder 28 has the greatest thickness and singly supports the vane 35 for rotation therewith by being secured thereto centrally intermediate the ends thereof that are disposed axially relative to the shaft 20. The vane holders v27 and 129 are paced apart in the referred to axial direction a distance equal to the width of the vane holder 28 and retain the vane 36 centrally intermediate the ends thereof that are disposed axially relative to the shaft 20. The juxtaposed annular radial outward surfaces of the vane holders 25-31 may be considered an inner wall for the housing 11 with an axis coincident with the axis of the shaft 20, hearing sleeve 21, chamber 12a, and outer cylindrical wall .12.

From FIG. 2 it is observed that the vane holders 26 and 30 retain the vane 37. The vane holders 2.5 and 31 retain the vane 38 by being secured to the vane 38 adjacent the respective edges thereof that are spaced axially relative to the shaft 20.

As shown in the drawings, the rotary vane motor includes a cup-shaped power rotor 40 (FIGS. 1 and 2). The power rotor 40 comprises a cylindrical Wall 41, which is disposed within the chamber 1211 between the inner surface of the cylindrical wall 12 of the housing 11 and the radially outward surfaces of the vane holders 25-31. As shown in FIG. 1, the cylindrical wall 41 of the rotor 40 has bores 42-45 formed therethrough. The bores 42-45 are disposed axially relative the fixed shaft and divide the cylindrical wall 41 into four separated segments 41a-41d.

Fitted within semi-cylindrical areas of the bores 42 and 43 of the segment 41b are semi-cylindroid bronze bearings 50 and 51, respectively (FIG. 1). Likewise, fitted within semi-cylindrical areas of the bores 43 and 44 of the segment 41c are semi-cylindroid bronze bearings 52 and 53, respectively. Similarly, fitted within the semicylindrical areas of the bores 44 and 45 of the segment 41d are semi-cylindroid bronze bearings 54 and 55, respectively. Lastly, fitted within the semi-cylindrical areas of the bores 45 and 42 of the segment 41a are semicylindroid bronze bearings 56 and 57.

The rotor vane 35 is disposed between and in engagement with the semicylindroid bearings 50 and 57. Thus, the power rotor 40 turns with the rotor vane 35 about the axis of the fixed shaft 20, while the semi-cylindroid bearings 50 and 57 thereof have radial sliding engagement with the rotor vane 35. In a like manner, the rotor vane 36 is disposed between and in engagement with the semi-cylindroids 51 and 52. Hen-cc, the power rotor 40 turns with the rotor vane 36 about the axis of the fixed shaft 20, whilet the semi-cylindroid bearings 51 and 52 thereof have radial sliding engagement with the rotor vane 36.

Similarly, the rotor vane 37 is disposed between and in engagement with the semi-cylindroid bearings 53 and 54. Therefore, the power rotor 40 turns with the rotor vane 37 about the axis of the fixed shaft 20, while the semi-cylindroid bearings 53 and 54 thereof have radial sliding engagement with the rotor vane 37. Lastly, the rotor vane 38 is disposed between and in engagement with the semi-cylindro-id bearings 55 and 56. The power rotor 40 turns with the rotor vane 38 about the axis of the fixed shaft 20, while the semi-cylindroid bearings 55 and 56 thereof have radial sliding engagement with the rotor vane 38. The semi-cylindroid bearings 51-56 are the only parts of the rotary vane motor that are subject to sliding friction under load, and hence, provide for inexpensive replacement parts to accommodate for wear.-

Integrally formed with the cylindrical wall 41 is a wall disc or plate 60 (FIG. 2) of the power rotor 40, which is disposed within the cylindrical bore 14a of the front cover plate 1 4 of the housing 1 1.

Projecting from the disc plate 60 in a direction oppos'ite from which the cylindrical wall 41 projects from the disc plate 60 is an integrally formed shaft 62 (FIG. 2) of the power rotor 40. The shaft 62 may at times function as a driven shaft for the device 10. The shaft 62, the disc plate 60 and the cylindrical wall 41 all of the power rotor 40 rotate in unison and turn with the rotor vanes 35-38 and the vane holders -31 about the axis of the fixed shaft 20.

As shown in FIG. 2, contained within the bore 14b of the front cover plate 14 and disposed between the wall surrounding the bore 14b and the rotatable shaft 62 of the power rotor 40 are a plurality of ball bearings 70. A collar '71 seated within the annular groove of the shaft 62 serves to retain the ball bearings 70 within the bore 14b. A thrust seal 72 (FIG. 2), which is disposed between the front cover plate 14 and the disc plate 60 of the power rotor 40, serves to permit adjustment of the power rotor 40 for the alignment of the cylindrical wall 4 41 of the rotor 40 with rotor vanes -38 and the front plate 14 of the housing 11. The rear cover plate 13 of the housing 11 forme a sealing engagement with the vanes 35-38 and the rearward face of the cylindrical wall 41.

According to the present invention, the ball bearings 70 (FIG. 1) rotate about a longitudinal axis offset with respect to the central axis of the cylindrical chamber 12a of the housing 11, the axis of the fixed shaft 20, and the axis of the housing 11, whereby the power rotor rotates about an axis offset from the just-described central axis. The axis of the fixed shaft 20, of the chamber 12a and the housing 11 are coincident.

Through this arrangement, the power rotor 40 rotates about an axis offset from the axis of the shaft 20, hearing sleeve 21 and the cylindrical chamber 12a. Thus, the space defined by successive vanes 35-38, respectively (FIG. 1), between the inner surface of the cylindrical wall 12 of the housing 11 and the radially outward surface of the cylindrical wall 41 of the power rotor 41) has a volumetric capacity varying sinusoidally as the power rotor 40 rotates in the direction of an arrow (FIG. 1). It is to be observed that the space defined by successive vanes 35-38, respectively, between the vane holders 25-31 and the radially inward surface of the cylindrical wall 41 of the power rotor 40 also varies cyclically in volumetric capacity as the power rotor 40 rotates in the direction of the arrow 80.

By virtue of the foregoing feature, the rotary vane motor 10 of the present invention by merely varying the locations of the ports thereof may be employed either as a two stage pneumatic compressor, a fixed ratio bifluid pump, a two stage pneumatic expansion motor or a two stroke cycle internal combustion engine.

Formed in the rear cover plate 13 of the housing 11 is an intake port (discontinued lines 81 (FIG. 1) show where the intake port meets the chamber 12a), which extends through the rear plate 13 axially and communicates with the chamber 12a between the bearing sleeve 21 and the inner surface of the cylindrical wall 41 of the power rotor 40. A carburator outlet, not shown, may be mounted on the rear cover plate 13 in registry with the intake port 81 for communication therewith.

An exhaust port 82 is formed in the cylindrical wall 12 of the housing 11 and communicates with the chamber 12a between the inner surface of the wall 12 and the radially outward surface of the cylindrical wall 41 of the power rotor 40.

An exhaust conduit 83 is attached to the wall 12 in registry with the port 82 for communication therewith. Also formed in the rear plate 13 of the housing 11 is a by-pass passage (discontinued lines 84 (FIG. 1) show where projections from the by-pass passage meet the chamber 12a), which serves to provide a path of fluid flow from the portion of the chamber 12a radially inward of the cylindrical wall 41 of the power rotor 40 to the portion of the chamber 12a radially outward of the cylindrical wall 41 of the power rotor 40. A spark plug 85 (FIG. 1) or any suitable igniting device is mounted on the cylindrical wall 12 of the housing 11 at an appropriate location to provide proper ignition timing and is connected to a suitable source of electrical energy, not shown.

In the operation of the rotary vane motor 10 as a two stroke cycle internal combustion engine, a fuel carburetor, not shown, feeds a mixture of fuel and air into the intake port (see dotted line 81 (FIG. 1)). From the intake port the mixture of fuel and air advances into the chamber 12a between the vane holders 25-31 and the radially inward surface of the cylindrical wall 41 of the power rotor 40. The discussion to follow will relate to a mixture of fuel and air received initially in the space between the rotary vanes 35 and 36.

It can be appreciated that during the operation of the rotary vane motor 10 the power rotor 40 will be rotating continuously in the direction of the arrow 80 and the mixture of fuel and air will be fed successively to the areas defined by successive rotary vanes in a continuous and uninterrupted manner.

As the rotary vane 36 advances in the direction of the arrow 80 and approaches the by-pass passage (see discontinued lines 84), the mixture of fuel and air drawn in through the intake port is compressed. Since the roller bearings support the power rotor 40 for rotation about an axis oifset from the axis of the cylindrical chamber 12a, the segment 41b of the cylindrical wall 41 of the power rotor 40 slides along the vanes 35 and 36 toward the axis of the cylindrical chamber 12a in a substantially sinusoidal manner (FIG. 1). As the vane 36 approaches the by-pass passage, the mixture of fuel and air drawn in through the intake port is compressed. When the leading rotor vane 36 advances beyond the intake side of the by-pass passage, the compressed mixture of fuel and air between the rotary vanes 36 and 35 is removed therefrom and enters the area defined by the inner surface of the cylindrical wall 12 of the housing 11 and the outer surface of the intermediate cylindrical wall 41 of the power rotor 40 between the rotary vanes 36 and 37 until the trailing vane 35 advances beyond the intake side of the by-pass passage. The above operation is occuring continuously and successively for successively advancing areas between successive vanes.

Subsequently, the leading vane 37 approaches the intake port and has completed a stroke of a cycle. As the leading vane 37 advances beyond the intake port 81 toward the spark plug 85, a gap or space always remains between the outer surface of the segment 410 of the cylindrical wall 41 of the rotor 40 and the inner surface 12a of the stationary cylindrical wall 12 of the stator to maintain a chamber between the vanes 37 and 36 for advancing the bypassed mixture of fuel and air compressed to combustion pressures into the combustion chamber where the spark plug 85 is located, although the outer walls 37a and 36a of the vanes 37 and 36, respectively, remain in sealing engagement with the inner surface 120! of the cylindrical wall 12. Similar successively advancing gaps between the succeeding outer sur faces of the segments of the cylindrical wall 41 of the rotor 40 and the inner surface 12a of the stationary cylindrical wall 12 of the stator are present so as to enable the by-passed mixture of fuel and air under combustion pressures to advance to the combustion chamber in which the spark plug 85 is located. At the outset of the second stroke of a cycle, the leading vane 37 is approaching the spark plug 85 and the by-passed mixture of fuel and air is compressed to combustion pressures. Here again, it is to be observed that since the ball or roller bearings 70 support the power rotor 40 for rotation about an axis offset from the axis of the cylindrical chamber 12a, the segment 41:: of the cylindrical wall 41 of the power rotor 40 slides along the vanes 36 and 37 first away from and then toward the axis of the cylindrical chamber 12a in substantially a sinusoidal manner (FIG. 1). As the vane 37 approaches the spark plug 85 the mixture of fuel and air is compressed to combustion pressures to be ignited during the second stroke. As the leading vane 37 ad vances beyond the spark plug 85, the continuously firing spark plug ignites the mixture of fuel and air compressed to combustion pressures. The ignition timing is a function of spark plug location and the firing occurs immediately prior to the minimum volume portion or top dead center.

The power or second stroke continues until the leading vane 37 advances beyond the exhaust port 82. At this time, internal pressures cause the gases to leave the chamber 12a through the exhaust port 82 in a continuous manner until the trailing vane 36 advances beyond the exhaust port 82, thus completing one firing cycle. The expanding gases of the ignited mixture impart a force on the leading vane to cause the vane to rotate in the direction of rotation of the power rotor. This continuous action in turn causes the drive shaft 62 of the power rotor 40 to rotate continuously.

It is to be observed that the leading vane 37 is approaching the intake port area to take on a fresh supply of mixture of fuel and air as the venting of the exhaust gases is being completed. The above operation is continuous as the rotor 40 continuously rotates and a mixture of fuel and air is fed to the intake port.

In the internal combustion engine of the present invention misfiring is eliminated by exposure of the compressed mixture of fuel and air to the continuously firing spark plug during substantially the entire power stroke instead of the normal single spark charge or pulse.

It is to be understood that modifications and variations of the invention disclosed herein may be resorted to with out departing from the spirit of the invention and the scope of the appended claims.

Having thus described my invention, what I claim as new and desire to protect by Letters Patent is:

l. A rotary vane motor comprising a housing with a stationary cylindrical outer wall, a rotatable inner wall spaced radially inward from said outer cylindrical wall concentric therewith, means carried by said housing to support said inner wall for rotation, a rotor with a rotatable intermediate cylindrical wall disposed between said inner and outer walls, said rotatable intermediate wall being formed with a plurality of axially disposed angularly spaced separation areas, an axially extending vane disposed in each of said separation areas, said housing being formed with a by-pass passageway communicating with the space between said outer wall and said intermediate wall and communicating with the space between said inner wall and said intermediate wall, means projecting from said inner wall and supporting said vanes for rotation about an axis coincident with the axis of said inner and outer walls, means carried by said housing to support said rotor for rotating said intermediate wall thereof about an axis offset from said axis coincident with said inner and outer walls, and means adapted for imparting movement to said vanes and said intermediate wall to turn said intermediate wall with said vanes and to move said intermediate wall in sliding engagement with said vanes in the radial direction.

2. A rotary vane internal combustion engine comprising a housing with .a stationary outer wall, a rotatable inner wall spaced radially inward from said outer cylindrical wall concentric therewith, means carried by said housing to support said inner wall for rotation, a rotor with a rotatable intermediate cylindrical wall disposed between said inner and outer walls, said rotatable intermediate wall being formed with a plurality of separation areas, an axially extending vane disposed in each of said separation areas, means projecting from said inner Wall and supporting said vanes for rotation about an axis coincident with the axis of said inner and outer walls, means carried by said housing to support said rotor for rotating said intermediate Wall thereof about an axis offset from said axis coincident with said inner and outer walls, intake means on said housing for directing an ignitable mixture into chambers between said inner wall and said intermediate wall between successive vanes in a successive sequence, said housing being formed with a by-pass passageway spaced from said intake means for directing the mixture in succession from the chambers between said inner wall and said intermediate wall to chambers between said outer wall and said intermediate wall, rotation of said vanes and said intermediate wall turns said intermediate wall with said vanes and moves said intermediate wall in sliding engagement with said vanes in the radial direction for compressing said mixtures to combustion pressures, and means on said housing to ignite said mixtures under combustion pressures to impart rotation to said vanes and said intermediate wall for rotating said rotor.

3. A rotary vane internal combustion engine comprising a housing with an outer cylindrical wall and an inner wall spaced radially inward from said outer cylindrical wall concentric therewith, a rotor with a rotatable intermediate cylindrical wall disposed between said inner and outer cylindrical walls, said rotatable intermediate wall being formed with a plurality of axially disposed angularly spaced separation areas, an axially extending vane disposed in each of said separation areas, means carried by said housing for supporting said vanes for rotation about an axis coincident with said inner and outer walls, means carried by said housing for supporting said rotor to rotate said intermediate wall for rotation about an axis offset from said axis coincident with said inner and outer walls, intake means on said housing for directing an ignitable mixture into chambers between said inner wall and said intermediate Wall between successive vanes in .a successive sequence, said housing being formed with a bypass passageway spaced from said intake means for directing the mixtures in succession from the chambers between said inner wall and said intermediate wall to chambers between said outer wall and said intermediate wall, 'rotation of said vanes and said intermediate wall turns said intermediate wall with said vanes and moves said intermediate wall in sliding engagement with said vanes in the radial direction for compressing said mixtures to combustion pressures, andmeans on said housing to ignite said mixtures under combustion pressures to impart rotation to said vanes and said intermediate wall for rotating said rotor.

4. A rotary vane internal combustion engine comprising a housing with an outer cylindrical wall and an inner wall spaced radially inward from said outer cylindrical wall concentric therewith, a rotor with a rotatable inter- 8 mediate cylindrical wall disposed between said inner and outer walls, said rotatable intermediate wall being formed with a plurality of axially disposed angularly spaced separation areas, an axially extending vane disposed in each of said separation areas, means carried by said housing for supporting said vanes for rotation, means carried by said housing for supporting said rotor to rotate said intermediate wall for varying cyclically in volumetric capacity each chamber between successive vanes and between said outer wall and said intermediate wall, means for directing ignitable mixtures into said chambers in a successive sequence, rotation of said vanes and said intermediate wall turns said intermediate wall with said vanes and moves =said intermediate wall in sliding engagement with said vanes in the radial direction for compressing said mixtures to combustion pressures, and means on said housing to ignite said mixtures under combustion pressures to impart rotation to said vanes and said intermediate wall for rotating said rotor.

KARL J. ALBRECHT, Primary Examiner.

JOSEPH H. BRANSON, JR., Examiner. 

1. A ROTARY VANE MOTOR COMPRISING A HOUSING WITH A STATIONARY CYLINDRICAL OUTER WALL, A ROTATABLE INNER WALL SPACED RADIALLY INWARD FROM SAID OUTER CYLINDRICAL WALL CONCENTRIC THEREWITH, MEANS CARRIED BY SAID HOUSING TO SUPPORT SAID INNER WALL FOR ROTATION, A ROTOR WITH A ROTATABLE INTERMEDIATE CYLINDRICAL WALL DISPOSED BETWEEN SAID INNER AND OUTER WALLS, SAID ROTATABLE INTERMEDIATE WALL BEING FORMED WITH A PLURALITY OF AXIALLY DISPOSED ANGULARLY SPACED SEPARATION AREAS, AN AXIALLY EXTENDING VANE DISPOSED IN EACH OF SAID SEPARATION AREAS, SAID HOUSING BEING FORMED WITH A BY-PASS PASSAGEWAY COMMUNICATING WITH THE SPACE BETWEEN SAID OUTER WALL AND SAID INTERMEDIATE WALL AND COMMUNICATING WITH THE SPACE BETWEEN SAID INNER WALL AND SAID INTERMEDIATE WALL, MEANS PROJECTING FROM SAID INNER WALL AND SUPPORTING SAID VANES FOR ROTATION ABOUT AN AXIS COINCIDENT WITH THE AXIS OF SAID INNER AND OUTER WALLS, MEANS CARRIED BY SAID HOUSING TO SUPPORT SAID ROTOR FOR ROTATING SAID INTERMEDIATE WALL THEREOF ABOUT AN AXIS OFFSET FROM SAID AXIS COINCIDENT WITH SAID INNER AND OUTER WALLS, AND MEANS ADAPTED FOR IMPARTING MOVEMENT TO SAID VANES AND SAID INTERMEDIATE WALL TO TURN SAID INTERMEDIATE WALL WITH SAID VANES AND TO MOVE SAID INTERMEDIATE WALL IN SLIDING ENGAGEMENT WITH SAID VANES IN THE RADIAL DIRECTION. 